Fastening component

Abstract

A fastening component (10, 50) has a thread forming portion (11, 51) and a seating surface forming portion (12, 52). The seating surface (12a, 52a) forming portion has a flange (122, 522) at a position near the seating surface, which flange is formed in a shape that expands outward in a radial direction and is configured to exert a compressive force on the target fastening component. The flange has an inclined surface (122c, 122d) on a surface opposite to the seating surface, which inclined surface is inclined so as to approach the seating surface toward an outside in the radial direction.The inclined surface has an inner inclined surface (122c) and an outer inclined surface (122d) located outside the inner inclined surface in the radial direction and having a larger angle of inclination relative to the support surface than the inner inclined surface.

Description

Technical FieldThis disclosure relates to a fastening member.Prior ArtJapanese Patent No. 6400647 discloses that a circular recess is provided on a washer for use in a fastening member provided between a vehicle component and a vehicle structural body. This configuration is disclosed to allow for strengthening the attachment and thereby improving vehicle handling stability.SUMMARY OF THE INVENTIONAccording to the above technique, the vehicle weight increases as a washer is added to the fastening member. As a means for strengthening the fastening without using a washer, a fastening member having a flange (e.g., flanged bolt and flanged nut) may be used. However, in order to increase the rigidity / strength of the flanged bolt, the thickness of the flange must be increased to reinforce the fastening. As a result, the weight of the flanged bolt increases accordingly.The present disclosure has been made in view of such a related art and intended to provide a fastening member capable of strengthening fastening while restraining an increase in weight.This object is achieved by a fastening component according to claim 1 or 10.According to claim 1, the outer inclined surface has an inclination angle larger than that of the inner inclined surface. The outer inclined surface is located outside the inner inclined surface in the radial direction. Thereby, in the flange, the thickness of the radially inner portion significantly contributing to the rigidity can be effectively increased. As a result, in the flange, an increase in a thickness of the radially outer portion where the stress in the axial direction is low can be suppressed. As a result, an increase in the weight of the fastening member can be suppressed.According to claim 10, a recess is formed in the flange on the surface opposite to the support surface. Thereby, a concentration point of internal stress can be generated in the flange upon fastening to the recess. Thereby, a fixation can be strengthened more than when the concentration point of the internal stress in the flange exists only in the innermost radial portion of the flange. Further, the recess is formed in such a manner that the outermost edge of the recess is closest to the support surface in the radial direction. Thereby, a decrease in the rigidity of the flange due to the formation of the recess can be minimized.As described above, according to the above aspects, it is possible to provide a fastening member that reinforces the fastening while suppressing weight increase.Further features and advantages follow from the description of embodiments with reference to the figures, of which:Brief Description of the DrawingsFIG. 1 is a cross-sectional view in an axial direction showing a fixing structure in the first embodiment; FIG. 2 is a cross-sectional view in the axial direction of an enlarged flange of FIG. 1 ; FIGS. 3(a)-3(c) are views showing the results of stress analysis of the first embodiment; FIG. 4 is a cross-sectional view in the axial direction showing the flange of the fixing structure in the second embodiment; FIG. 5 is a cross-sectional view in the axial direction showing the flange of the fixing structure in the third embodiment; FIG. 6 is a cross-sectional view in the axial direction showing the fixing structure in the fourth embodiment.Detailed Description of the Preferred EmbodimentsA fastening member includes a thread formation portion and a support surface formation portion. The support surface forming portion includes a flange formed at a position near the support surface in a shape expanding outward in a radial direction and configured to apply a pressing force to a target fastening member. The flange has an inclined surface on the surface opposite to the support surface. The inclined surface is inclined so as to approach the support surface from the inner side to the outer side in the radial direction. The inclined surface has an inner inclined surface and an outer inclined surface. The outer inclined surface is located outside the inner inclined surface in the radial direction and has a larger inclination angle relative to the support surface than the inner inclined surface.In the fixing member, a boundary between the inner inclined surface and the outer inclined surface may be located within an outermost support portion configured to abut on the target fixing member at an outermost position in the radial direction of the support surface. The inclination angle changes at the boundary. Thereby, in the flange, an increase in thickness of an outer side portion in the radial direction where the stress in the axial direction is low can be effectively suppressed.In the fixing member, the inner inclined surface may have an inclination angle of 20° to 30°, and the outer inclined surface may have an inclination angle of 35° to 50°. Thereby, in the flange, the thickness of the radially inner portion significantly contributing to rigidity can be effectively increased. In addition, an increase in the thickness of the radially outer portion where the stress in the axial direction is small can be effectively suppressed.In the fixing member, the flange may have a recess formed between the inner inclined surface and the outer inclined surface on the surface opposite to the support surface. Thereby, a concentration point of internal stress may be generated in the flange during fastening to the recess. As a result, the fixation can be more strengthened than when the concentration point of the internal stress is generated in the flange only at the innermost radial portion of the flange.In the fixing member, the recess may be formed within the outermost support portion configured to abut on the target fixing member at an outermost position in the radial direction. Thereby, the concentration point of the internal stress generated by the recess can effectively exert a stress in the axial direction on the target mounting member. As a result, the attachment can be strengthened.In the fastening member, the recess has a shape obtained by notching the surface of the flange opposite to the support surface to have an L shape in an axial cross section. Thereby, the decrease in rigidity of the flange due to the recess can be suppressed. Further, the concentration point of the internal stress in the flange during fastening can be effectively generated at the recess.In the fastening member, the recess may be formed in a shape in which an outermost edge of the recess is closest to the support surface in the radial direction. Thereby, the decrease in rigidity of the flange due to the recess can be suppressed.In the fixing member, the recess may be formed in the flange between the innermost portion and the outermost support portion in the radial direction. The innermost portion of the flange is located at an innermost position in the radial direction of the flange. The outermost support portion of the flange abuts on the target fastening member at the outermost position in the radial direction. Further, the recess may be formed in the flange between the outermost radial portion and the innermost radial portion in an axial direction. The outermost radial portion of the flange is located at an outermost position in the radial direction. Thereby, the decrease in rigidity of the flange due to the recess can be suppressed. Further, a concentration point of internal stress in the flange during fastening can be effectively generated at the recess.In the fastening member, the recess may be configured to intersect a virtual line. The virtual line divides (bisects) a radial distance between the innermost radial portion and the outermost support portion and is parallel to the axial direction. Thereby, the decrease in rigidity of the flange due to the recess can be suppressed. Further, the concentration point of the internal stress in the flange during fastening can be effectively generated at the recess.In the fastening member, the inner inclined surface and the outer inclined surface may be formed in a linearly tapered shape in a cross section in the axial direction. Thereby, in the flange, the thickness of the radially inner portion significantly contributing to the rigidity can be effectively increased. Further, in the flange, the increase in the thickness of the radially outer portion where the stress in the axial direction is low can be effectively suppressed.First Embodiment1. Configuration of Fixing Structure 1A fixing structure 1 in the first embodiment will be described with reference to FIGS. 1 to 3. In the mounting structure 1, a rear absorber (shock absorber) constituting a chassis component of a car is fixed to the body of the car using a first mounting member 10.The fixing structure 1 in the first embodiment includes the first fixing member 10, a second fixing member 20, a first target fixing member 30, and a second target fixing member 40, as shown in FIG. 1. In the fixing structure 1, the first fixing member 10 and the second fixing member 20 are used to fix the first target fixing member 30 and the second target fixing member 40. In the first embodiment, the first target mounting member 30 is, for example, a steel plate constituting a body of a car, and the second target mounting member 40 is, for example, a bracket for fixing a rear absorber of a car to the body of the car.As shown in FIG. 1, the first fastening member 10 is a bolt that extends in an axial direction Y and includes a thread formation portion 11 and a bearing surface formation portion 12. In the first embodiment, the first fastening member 10 is, for example, a bolt having a thread diameter (nominal diameter) of 10 mm. The thread formation portion 11 is a bolt shaft having an external thread 11 aextending in the axial direction Y. The support surface forming portion 12 is a bolt head and has a support surface 12 athat abuts on the second target fastening member 40. The bearing surface forming portion 12 is provided in a coaxial manner with the thread forming portion 11 and has a larger extension in the radial direction than the thread forming portion 11. the external thread 11 aof the thread forming portion 11 may be formed only in the central portion of the thread forming portion 11 as shown in FIG. 1 or over the entire length of the thread forming portion 11 even if not shown.The first fastening component 10 is a flanged bolt. The bearing surface forming portion 12 of the first fastening member 10 is a flanged bolt head. Specifically, the support surface forming portion 12 includes a head main body 121 and a flange 122. In the first embodiment, the head main body 121 is formed in the shape of a hexagonal head, but the head main body 121 may be formed in a shape other than a hexagonal shape and may be formed in the shape of an inner hexagon or a cross slot. The flange 122 is formed in a shape that expands outward in a radial direction perpendicular to the axial direction Y over the entire circumference of the support surface forming portion 12 at a position near the support surface 12 a, and is configured to apply a pressing force to the second target fastening member 40. The support surface 12 aof the support surface forming portion 12 is formed in a continuous manner by the lower surface of the head main body 121 and the lower surface of the flange 122.In the first embodiment, the width of planar surfaces of the head main body 121 of the support surface forming portion 12 (diameter of the inner circle of the head main body 121) is larger than the diameter of the thread forming portion 11. the diameter of the flange 122 of the support surface forming portion 12 is larger than the diameter of the thread forming portion 11 and the width of planar surfaces of the head main body 121.The second fastening member 20 is, for example, a nut provided with an internal thread configured to be screwed on the external thread 11 aof the first fastening member 10. In the first embodiment, the second fastening member 20 is a weld nut that is pre-welded to the first target fastening member 30. A flanged nut separate from the first target fastening member 30, or a nut without a flange separate from the first target fastening member 30, may be used as the second fastening member 20.2. Detailed Configuration of Seating Surface Forming Portion 12 of First Fastening Member 10Hereinafter, the portion on the support surface 12 aof the support surface formation portion 12 configured to abut on (a surface of) the second target mounting member 40 at the outermost position in the radial direction is defined as an outermost support portion 122 a. As shown in FIG. 2, the flange 122 has a fillet 122 bformed near the support surface 12 aand outside the outermost support portion 122 ain the radial direction when the first fastening member 10 is molded.In the flange 122, the surface facing the support surface 12 ais inclined as a whole so as to approach the support surface 12 atowards the outer in the radial direction. Hereinafter, the surface opposite to the support surface 12 ais defined as an inclined surface.The inclined surface of the flange 122 includes an inner inclined surface 122 c, an outer inclined surface 122 d, and a recess 122 e. The inner inclined surface 122 cis connected to the head main body 121. The outer inclined surface 122 dis located outside the inner inclined surface 122 cin the radial direction. In other words, the inner inclined surface 122 cis located radially inward on the inclined surface of the flange 122, and the outer inclined surface 122 dis located radially outward on the inclined surface of the flange 122.Hereinafter, an inclination angle relative to the support surface 12 awhich is an acute angle is simply defined as the inclination angle. The inclination angle of the outer inclined surface 122 dis larger than that of the inner inclined surface 122 c. The inclination angle of the inner inclined surface 122 cis preferably 20° to 30°, and the inclination angle of the outer inclined surface 122 dis preferably 35° to 50°. In the first embodiment, the inclination angle of the inner inclined surface 122 cis 25° and the inclination angle of the outer inclined surface is 40°.In the first embodiment, the outer inclined surface 122 dis formed up to an outermost radial portion 122 fof the flange 122. The flange 122 has a predetermined thickness t 1 between the outermost radial portion 122 fand the support surface 12 a.By setting the inclination angle of the outer inclined surface 122 dto be larger than that of the inner inclined surface 122 c, the following effects can be obtained. In the flange 122, the thickness at the position near the head main body 121 that significantly contributes rigidity (rigidity) can be increased. As a result, the rigidity of the flange 122 can be increased. Further, the increase in the thickness of the outer side portions in the radial direction of the flange 122 where the stress in the axial direction is small can be suppressed. As a result, the increase in the weight of the first fastening member 10 can be suppressed.The recess 122e is formed in the inclined surface of the flange 122. The recess 122 eis formed in a circular shape over the entire circumference of the flange 122. In the first embodiment, the recess 122 is formed at the boundary between the inner inclined surface 122 cand the outer inclined surface 122 d. In other words, the recess 122 eis connected to the inner inclined surface 122 cat an inner position in the radial direction and is connected to the outer inclined surface 122 dat an outer position in the radial direction.In the first embodiment, the inclined surface of the flange 122 has a step shape formed by the recess 122 e. The recess 122 ehas a shape obtained by notching the inclined surface of the flange 122 in an L shape in an axial cross section. Specifically, the recess 122 ehas a wall surface extending from a connection portion 122 gadjacent to the inner inclined surface 122 cin a direction almost parallel to the axial direction Y of the first fastening member 10, and a bottom surface extending from a connection portion 122 hadjacent to the outer inclined surface 122 din a direction almost perpendicular to the axial direction Y of the first fastening member 10. As a result, the recess 122 eapproaches the support surface 12 atoward the outer side in the radial direction, and an outermost edge of the recess 122 ecomes closest to the support surface 12 a.The recess 122 eis formed within the virtual rectangle S 1 shown by a two-dot chain line in FIG. 2. Specifically, the recess 122 eis formed between an innermost radial portion 122 iand the outermost support portion 122 aof the flange 122 in the radial direction of the first fastening member 10. The recess 122 eis formed between the innermost radial portion 122 iand the outermost radial portion 122 fof the flange 122 in the axial direction Y of the first fastening member 10.In the first embodiment, the recess 122 eis configured to intersect a virtual line L 1. The virtual line L 1 bisects (divides) a radial distance between the innermost radial portion 122 iand the outermost support portion 122 a, and is parallel to the axial direction Y.By forming the recess 122 ein the flange 122, a concentration point of internal stress in the flange 122 can be generated at the recess 122 ewhen the first fastening member 10 and the second fastening member 20 fasten the first target fastening member 30 and the second target fastening member 40. Thereby, a moment generated when an external force that pulls the second target fastening member 40 away from the first target fastening member 30 acts on the outermost radial portion of the second target fastening member 10 can be reduced as compared with the case where the concentration point of the internal stress in the flange 122 exists only at the innermost radial portion 122 iof the flange 122. Thereby, the fixation between the first target fixation member 30 and the second target fixation member 40 can be strengthened by the first fixation member 10 and the second fixation member 20.3. Analysis of Mounting Structure 1The analysis of the fixing structure 1 will be described with reference to FIGS. 3(a)-3(c). The analysis results of an analysis example 1 corresponding to the first embodiment, an analysis example 2, and an analysis example 3 are respectively shown in FIGS. 3( a), 3( b), and 3( c).The analysis models used in Analysis Examples 1-3 are each three-dimensional models including the first mounting member 10, the first target mounting member 30, and the second target mounting member 40.In Analysis Example 1 shown in FIG. 3( a), an analysis model was used in which the inclination angle of the inner inclined surface 122 cis 25°, the inclination angle of the outer inclined surface 122 dis 40°, and the recess 122 eis formed.In Analysis Example 2 shown in FIG. 3( b), an analysis model was used in which the inclination angle of the inclined surface of the flange 122 is 25° throughout without change and the recess 122 eof the first embodiment is not formed in the flange 122.In Analysis Example 3 shown in FIG. 3( c), an analysis model was used in which the inclination angle of the inclined surface of the flange 122 is 25° throughout without change and the recess 122 eis formed in the flange 122 similarly to that in the first embodiment.In the analysis models used in Analysis Examples 1-3, the first target fixing member 30 is made of structural steel and the second target fixing member 40 is made of an aluminum alloy. The first fastening member 10 has a Young's modulus (Young's modulus) of 206 GPa, a Poisson's ratio (Poisson's ratio) of 0.3, and a yield stress of 1017 MPa.In these analysis models, an axial force generated in the first fixing member 10 is 38.6 kN, and a load of 8.4 kN is applied to the outermost radial portion of the second target fixing member 40 in a direction for peeling the second target fixing member 40 from the first target fixing member 30. The analysis results of Analysis Examples 1-3 in FIGS. 3(a) to 3(c) are shown in an axial direction voltage contour graph, showing a higher voltage with a darker color.Comparing Analysis Example 2 shown in FIG. 3( b) and Analysis Example 3 shown in FIG. 3( c), an effect of the recess 122 eon the stresses in the axial direction can be seen. Comparing Analysis Example 3 shown in FIG. 3( c) and Analysis Example 1 shown in FIG. 3( a), an effect of setting the inclination angle of the outer inclined surface 122 dto a value larger than that of the inclination angle of the inner inclined surface 122 cmay be seen.In Analysis Example 2 shown in FIG. 3( b), a concentration point of stress in the axial direction is generated at the innermost radial portion 122 iof the flange 122. However, the stress in the axial direction transmitted to the outer side portion of the flange 122 in the radial direction is small.In contrast, in Analysis Example 3 shown in FIG. 3( c), since the recess 122 eis formed in the flange 122, the concentration point of the stress in the axial direction is generated in the flange 122 not only at the innermost radial portion 122 iof the flange 122, but also at the recess 122 e. Thereby, the stress in the axial direction transmitted to the outer side portion of the flange 122 in the radial direction is larger compared to Analysis Example 2. However, in Analysis Example 3 shown in FIG. 3( c), the axial stress transmitted to the vicinity of the inclined surface of the flange 122 outside the recess 122 ein the radial direction is still small with hardly any change compared to Analysis Example 2.In the analysis example 1 shown in FIG. 3( a), the inclination angle of the outer inclined surface 122 dis set to be larger than that of the inner inclined surface 122 c. Due to such a configuration, the portion where the stress in the axial direction is less outside the recess 122 ein the radial direction can be removed, thereby achieving weight reduction. From the above description, it is understood that Analysis Example 1 corresponding to the first embodiment enables strengthening of the fixation between the first target fixation member 30 and the second target fixation member 40 without increasing the weight.4. Operational AdvantageIn the first fastening member 10 according to the first embodiment, the outer inclined surface 122 dof the flange 122 of the first fastening member 10 has a larger inclination angle than the inner inclined surface 122 c. Thereby, in the flange 122, a thickness of a portion close to the head main body 121 that substantially contributes to the rigidity can be effectively increased. As a result, the rigidity of the flange 122 can be increased. In addition, an increase in the thickness of the flange 122 at the radially outer portion where the stress in the axial direction is low can be suppressed. As a result, the increase in the weight of the first fastening member 10 can be suppressed. Thereby, the fastening by the first fastening member 10 can be strengthened while suppressing the increase in the weight of the first fastening member 10.In the first fastening member 10 according to the first embodiment, the boundary between the inner inclined surface 122 cand the outer inclined surface 122 dis located inside the outermost support portion 122 ain the radial direction. The inclination angle changes at the boundary. Thereby, in the flange 122, the increase in a thickness of the outer side portion in the radial direction at which the stress in the axial direction is low can be effectively suppressed.In the first fastening member 10 according to the first embodiment, the inner inclined surface 122 chas an inclination angle of 20° to 30°, and the outer inclined surface 122 dhas an inclination angle of 35° to 50°. Thereby, in the flange 122, the thickness of a portion close to the head main body 121 that substantially contributes to the rigidity can be effectively increased. In addition, in the flange 122, the increase in the thickness of the radially outer portion where the stress in the axial direction is low can be effectively suppressed.In the first fixing member 10 according to the first embodiment, the recess 122 eis formed in the inclined surface of the flange 122. Thereby, the concentration point of the internal stress can be generated in the flange 122 during the fastening to the recess 122 e. Thereby, the fixation can be stronger than when the concentration point of the internal stress in the flange 122 exists only at the innermost radial portion 122 iof the flange 122.In the first fastening member 10 according to the first embodiment, the recess 122 eis formed inside the outermost support portion 122 aof the flange 122 in the radial direction. Thereby, the concentration point of the internal stress generated by the recess 122 ecan effectively apply a stress in the axial direction to the second target mounting member 40. As a result, the attachment can be strengthened.In the first fastening member 10 according to the first embodiment, the recess has a shape obtained by notching the inclined surface to have an L shape in an axial cross section. Thereby, the lowering of the rigidity of the flange 122 due to the recess 122 ecan be prevented. Further, the concentration point of the internal stress in the flange 122 during the fastening can be effectively generated at the recess 122 e.In the first fastening member 10 according to the first embodiment, the recess 122 eis formed in a shape in which the outermost edge of the recess 122 eis closest to the support surface 12 ain the radial direction. Thereby, the decrease in rigidity of the flange 122 due to the recess 122 ecan be suppressed.In the first fastening member 10 according to the first embodiment, the recess 122 eis formed in the flange 122 between the innermost radial portion 122 iand the outermost support portion 122 ain the radial direction. Further, the recess 122 eis formed in the flange 122 between the outermost radial portion 122 fand the innermost radial portion 122 iin the axial direction. Thereby, the decrease in rigidity of the flange 122 due to the recess 122 ecan be suppressed. Further, the concentration point of the internal stress of the flange can be effectively generated at the recess 122 eduring the fastening of the flange 122.In the first fixing member 10 according to the first embodiment, the recess 122 eis configured to intersect the virtual line L 1. The virtual line L 1 bisects the radial distance between the innermost radial portion 122 iand the outermost support portion 122 aof the flange 122, and is parallel to the axial direction Y. Thereby, the decrease in rigidity of the flange 122 due to the recess 122 ecan be suppressed. Further, the concentration point of the internal stress of the flange 122 during the fastening of the flange 122 can be effectively generated at the recess 122 e.In the first fastening member 10 according to the first embodiment, the inner inclined surface 122 cand the outer inclined surface 122 dare formed in a linearly tapered shape in a cross section in the axial direction. Thereby, in the flange 122, the thickness of the radially inner portion significantly contributing to the rigidity can be effectively increased. Further, in the flange 122, the increase in the thickness of the radially outer portion where the stress in the axial direction is low can be effectively suppressed.Second EmbodimentIn the first embodiment above, the recess 122 ehas the shape obtained by notching the inclined surface of the flange 122 in the L shape in the axial cross section, while in the second embodiment, as shown in FIG. 4, the recess 122 kformed in the inclined surface of the flange 122 has, in the axial cross section, a shape obtained by notching the inclined surface of the flange 122 in an arc shape.In the cross section in the axial direction of the flange 122, a tangential line (not shown) of the recess 122 kas the connecting portion 122 hwith the outer inclined surface 122 dis parallel to the support surface 12 a. Thereby, the recess 122 kis formed to approach the support surface 12 atoward the outer side in the radial direction. Further, the recess 122k is formed to be closest to the support surface 12a at the outermost edge of the recess 122k.Also in the second embodiment, similarly to the first embodiment, the recess 122 kis formed in the inclined surface of the flange 122, so that the concentration point of the internal stress may be generated in the flange 122 during the fastening to the recess 122 k. Thereby, the fixation can be made stronger than when the concentration point of the internal stress in the flange 122 exists only at the innermost radial portion 122 iof the flange 122.Third EmbodimentIn the first and second embodiments, the inner inclined surface 122 c, the outer inclined surface 122 d, and the recesses 122 eand 122 kare formed in the inclined surface of the flange 122, while in the third embodiment, as shown in FIG. 5, the recesses 122 eand 122 kare not formed in the inclined surface of the flange 122, and only the inner inclined surface 122 cand the outer inclined surface 122 dare formed therein.Also in the third embodiment, similar to the first and second embodiments, an operational advantage of the inner inclined surface 122 cand the outer inclined surface 122 dmay be achieved. Specifically, the outer inclined surface 122 dof the flange 122 has a larger inclination angle than the inner inclined surface 122 c. Thereby, in the flange 122, the thickness at the position closer to the head main body 121 and significantly contributing to the rigidity can be increased. As a result, the rigidity of the flange 122 can be increased. Further, the increase in the thickness of the radially outer portion of the flange 122 where the stress in the axial direction is small can be suppressed. Thereby, the increase in the weight of the first fastening member 10 can be suppressed. Consequently, the fastening with the first fastening member 10 can be strengthened while suppressing the increase in the weight of the first fastening member 10.Fourth EmbodimentIn the first embodiment, the first fastening member 10 is a flanged bolt, the second fastening member 20 is a nut, and the inner inclined surface 122 c, the outer inclined surface 122 d, and the recess 122 eare formed in the inclined surface of the flange 122 of the first fastening member 10. In contrast, in the fourth embodiment, as shown in FIG. 6, a first fastening member 50, a flanged nut, a second fastening member 60, a bolt and an inner inclined surface, an outer inclined surface, and a recess, all of which are the same as in the first embodiment, are formed in the inclined surface of the flanged portion 522 of the first fastening member 50.The second fastening member 60 may be a welding bolt previously welded to the first target fastening member 30, a flanged bolt separated from the first target fastening member 30, or a bolt without a flange separated from the first target fastening member 30.The first fastening member 50 includes a thread formation portion 51 and a support surface formation portion 52. The thread formation portion 51 has a portion located near a central axis in the first fastening member 50. On the thread formation portion 51, an internal thread 51 aextending in the axial direction Y is formed. The support surface forming portion 52 includes an outer peripheral portion of the fastening member 50. The support surface forming portion 52 has a support surface 52 aformed to abut on the second target fastening member 40. The support surface forming portion 52 includes a nut main body 521 and a flange 522. In the fourth embodiment, the nut main body has a hexagonal prism shape.The flange 522 is formed in a shape that extends outward in a radial direction perpendicular to the axial direction Y over the entire circumference of the support surface forming portion 52 at a position close to the support surface 52 aand applies a pressing force to the second target fastening member 40. The support surface 52 aof the support surface forming portion 52 is formed in a continuous manner by the bottom surface of the nut main body 521 and the bottom surface of the flange 522.On the surface opposed to the support surface 52 aof the flange 522, an inner inclined surface, an outer inclined surface, and a recess are formed in the same manner as in the first embodiment. Since the specific configurations of the inner inclined surface, the outer inclined surface, and the recess are the same as in the first embodiment, detailed description is omitted.Also in the fourth embodiment, the inner inclined surface, the outer inclined surface, and the recess configured in the same manner as in the first embodiment are formed in the flange 522 of the first fixing member 50, whereby the same operational advantage as in the first embodiment can be obtained.Other EmbodimentsIn the above embodiments, the inner inclined surface, the outer inclined surface, and the recess are formed only in the first fixing member among the first and second fixing members, but the inner inclined surface, the outer inclined surface, and the recess may be formed in both the first and second fixing members.In the above embodiments, the inner inclined surface and the outer inclined surface are formed in the inclined surface of the flange, and the inclination angle of the inclined surface changes in two steps toward the outer side in the radial direction, but the inclination angle of the flange may change in three or more steps. When the inclination angle of the inclined surface of the flange has three or more steps, the inclination angles of the two inclined surfaces located on both sides of the recess, respectively, do not necessarily need to be different, and the inclination angles of the two inclined surfaces located on both sides of the recess, respectively, may be the same.In the above-mentioned embodiments, the inclination angles of the inner and outer inclined surfaces of the flange are respectively constant and the inner and outer inclined surfaces are formed in a straight line when viewed in an axial cross section, but the inclination angle of at least one of the inner and outer inclined surfaces does not necessarily need to be constant and may be varied. In other words, at least one of the inner and outer surfaces may be curved when viewed in an axial cross section.It is expressly emphasized that all features disclosed in the description and / or the claims are to be regarded as separate and independent from each other for the purpose of original disclosure as well as for the purpose of restricting the claimed invention independently of the combinations of features in the embodiments and / or the claims. It is expressly stated that all range specifications or specifications of groups of units disclose every possible intermediate value or subgroup of units for the purpose of original disclosure as well as for the purpose of restricting the claimed invention, in particular also as a boundary of a range specification.Description of the Reference Numerals1 Fastening structure 10, 50 First fastening member 11, 51 Thread formation portion 11 a Außengewinde 12, 52 Support surface formation portion 12 a, 52 a Auflage surface 121 Head main body 122, 522 Flange 122 a Äußerst support portion 122 b Abrundung 122 cInner inclined surface 122 dOuter inclined surface 122 e, 122 k Ausnehmung 122 g, 122 h Verbindungs portion 122 f Äußerst radial portion 122 i Innerste radial portion 20, 60 Second fastening member 30 First target fastening member 40 Second target fastening member 51 a 521 Nut main body L 1 Virtual line Y Axial direction t 1 ThicknessReferences included in the specificationThis list of documents cited by the applicant has been produced in an automated manner and is only included for the better information of the reader. The list is not part of the German patent application or utility model application. The DPMA does not take any adhesion for any faults or omissions.Patent Literature citedJP 64006447

[0002]

Claims

A fastening member (10, 50) comprising a thread forming portion (11, 51) having an external thread (11a) or internal thread (51a) extending in an axial direction (Y) formed therein, and a support surface forming portion (12, 52) having a support surface (12a, 52a) formed to abut on a target fastening member (40), wherein the support surface forming portion (12, 52) has a flange (122, 522) at a position close to the support surface (12a, 52a), the flange (122, 522) being formed in a shape that extends outward in a radial direction perpendicular to the axial direction (Y) and configured to apply a pressing force to the target fastening member (40), the flange (122, 522) having an inclined surface (122c, 122d) on a surface opposite to the support surface (12a, 52a) in the axial direction, the inclined surface (122c, 122d) is inclined so as to approach the support surface (12a, 52a) toward an outer side in the radial direction, the inclined surface (122c, 122d) has an inner inclined surface (122c), and an outer inclined surface (122d) that is located farther outward in the radial direction than the inner inclined surface (122c) and that has a larger inclination angle relative to the support surface (12a, 52a) than the inner inclined surface (122c).The fastening member (10, 50) according to claim 1, wherein a boundary between the inner inclined surface (122c) and the outer inclined surface (122d) is located within an outermost support portion (122a) configured to abut on the target fastening member (40) at an outermost position in the radial direction on the support surface (12a, 52a).The fastening member (10, 50) according to claim 1 or 2, wherein the inner inclined surface (122c) has an inclination angle of 20° to 30°, and the outer inclined surface (122d) has an inclination angle of 35° to 50°.The fastening member (10, 50) according to any one of claims 1 to 3, wherein the flange (122, 522) has a recess (122e, 122k) formed between the inner inclined surface (122c) and the outer inclined surface (122d) on the surface opposite to the support surface (12a, 52a), and the recess (122e, 122k) is formed within an outermost support portion (122a) configured to abut on the target fastening member (40) at an outermost position in the radial direction.The fastening member (10, 50) according to claim 4, wherein the recess (122e, 122k) has a shape obtained by notching the surface opposite to the support surface (12a, 52a) in the flange (122, 522) to have an L-shape in an axial cross section.The fastening member (10, 50) according to claim 4, wherein the recess (122e, 122k) has a shape in which an outermost edge in the radial direction of the recess (122e, 122k) is closest to the support surface (12a, 52a).The fastening member (10, 50) according to any one of claims 4 to 6, wherein the recess (122e, 122k) is formed in the flange (122, 522) between an innermost radial portion (122i) located innermost in the radial direction and the outermost support portion (122a), and is formed in the axial direction between an outermost radial portion (122f) located outermost in the radial direction and the innermost radial portion (122i).The fastening member (10, 50) according to claim 7, wherein the recess (122e, 122k) is configured to cut a virtual line (L1) bisecting a radial distance between the innermost radial portion (122i) and the outermost support portion (122a) and parallel to the axial direction.The fastening member (10, 50) according to any one of claims 1 to 8, wherein the inner inclined surface (122c) and the outer inclined surface (122d) are formed in a linearly tapered shape in a cross section in the axial direction.A fastening member (10, 50) comprising a thread forming portion (11, 51) having an external thread (11a) or internal thread (51a) extending in an axial direction (Y) formed therein, and a support surface forming portion (12, 52) having a support surface (12a, 52a) formed to abut on a target fastening member (40), wherein the support surface forming portion (12, 52) has a flange (122, 522) at a position close to the support surface (12a, 52a), the flange (122, 522) being formed in a shape expanding outward in a radial direction perpendicular to the axial direction and configured to apply a pressing force to the target fastening member (40), the flange having a recess (122e, 122k), which is formed on a surface opposite to the support surface ( 12 a, 52 a) in the axial direction, and which recess ( 122 e, 122 k) has a shape in which an outermost edge in the radial direction of the recess ( 122 e, 122 k) is closest to the support surface ( 12 a, 52 a).A fastening structure comprising a first fastening member (10, 50) according to any one of claims 1 to 10, a second fastening member (20, 60) having a thread formation portion having an internal thread or an external thread configured to be screwed into or onto the corresponding external thread or internal thread of the first fastening member, a first target fastening member (30), and a second target fastening member (40) having a surface against which the support surface (12a, 52a) of the support surface formation portion (12, 52) abuts.The fixing structure according to claim 11, wherein the first fixing member and the second fixing member are formed as a bolt and a complementary nut for fixing an absorber member as the second target fixing member (40) to a plate member as the first target fixing member (30).

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